WO2008037644A1 - Mécanisme à manivelle pour pompe à mécanisme à manivelle et utilisation dans une pompe à carburant - Google Patents

Mécanisme à manivelle pour pompe à mécanisme à manivelle et utilisation dans une pompe à carburant Download PDF

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Publication number
WO2008037644A1
WO2008037644A1 PCT/EP2007/059932 EP2007059932W WO2008037644A1 WO 2008037644 A1 WO2008037644 A1 WO 2008037644A1 EP 2007059932 W EP2007059932 W EP 2007059932W WO 2008037644 A1 WO2008037644 A1 WO 2008037644A1
Authority
WO
WIPO (PCT)
Prior art keywords
lubricant
channel
bearing
crank drive
drive shaft
Prior art date
Application number
PCT/EP2007/059932
Other languages
German (de)
English (en)
Inventor
Wolfgang Bloching
Ümit Dilalan
Mario Köhler
Stephan Notzon
Original Assignee
Continental Automotive Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Continental Automotive Gmbh filed Critical Continental Automotive Gmbh
Publication of WO2008037644A1 publication Critical patent/WO2008037644A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0238—Hermetic compressors with oil distribution channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F04B53/144—Adaptation of piston-rods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/18—Lubricating

Definitions

  • crank drive for crank drive pump and use in a fuel pump
  • the present invention relates to an improvement in the La ⁇ ger lubrication of a crank mechanism for crankshaft pumps, which is intended for applications in fuel pumps.
  • the connecting rod also referred to briefly as the connecting rod, has two openings, namely the so-called connecting rod eye for receiving a piston pin, which connects via a piston rod to a linearly moving piston, for example, and an opening in the so-called connecting rod, which Crankshaft or on the crankshaft eccentrically arranged part receives.
  • crankshaft rotates within the respective opening of the connecting rod. Therefore, there is no rigid connection between the connecting rod and the crankshaft, but a suitable bearing between the mutually moving parts provided. In the operation of the device considerable forces act on the bearing. Such bearings are therefore exposed to high stresses and must be lubricated sufficiently well to minimize wear as little as possible.
  • sliding and roller bearings are used in conventional high-pressure pumps. In particular, in internal combustion engines ⁇ reindeer and Wasserpumpenbau the storage takes place in the connecting rod eye and on the crankshaft by means of a sliding bearing connection. Targeted lubrication of bearings in highly stressed fuel pumps is unknown.
  • Object of the present invention is to provide a reliable crank mechanism for crankshaft pumps, with which a good lubrication of the bearings is achieved.
  • This crank mechanism should be particularly suitable for use in fuel pumps.
  • the crank mechanism comprises a mechanically operating Kochtra ⁇ mounting part which is arranged on a drive shaft, wherein at least one bearing is provided between these parts.
  • the crank mechanism has, independently of the respective configuration of the moving parts, an arrangement of at least one lubricant channel, which opens between the drive shaft and the bearing and with which the lubricant can be passed directly to friction points between relatively moving parts, thereby achieving improved lubrication of the bearing becomes.
  • This crank drive allows for the first time an improved lubrication of the bearings in fuel pumps.
  • the drive shaft has in preferred embodiments, a main lubricant channel and at least one lubrication ⁇ karnebenkanal that connects between the lubricating central channel and the warehouse. This makes it possible to introduce a lubricant into the main lubricant channel and to lubricate the bearing directly in the region between the bearing and the drive shaft via the connection through the lubricant side channel.
  • Advantageous embodiments provide to provide a plurality of bearings of the drive shaft and the transmission part with such lubricant ⁇ medium channels , so that all bearings can be supplied directly with lubricant in the area between the mutually moving parts. In this way, a longer life of the crank mechanism can be achieved even at higher pressure loads.
  • Particular advantages are a ver ⁇ schl explicatarmer operation of the rubbing contact partner, the possibility of launching and transmission of higher forces, a more favorable bearing loads, a specific lubrication of each highly loaded regions of the bearing and the obtaining of a constant lubricant pressure at all operating points.
  • Advantageous embodiments provide to provide the bearing with a lubricating groove, which is provided in each case on the bearing or on the contact partner arranged thereon and allows improved distribution of the lubricant.
  • spe ⁇ essential to a fuel pump in particular a connecting rod ⁇ rod as a transmission part and a crankshaft is suitable as to ⁇ drive shaft.
  • the bearing is in this case vorzugswei ⁇ se also provided on a side facing away from the crankshaft side with a lubrication, so that the friction surface in the opening of the connecting rod is sufficiently provided with lubricant.
  • the bearing between the drive shaft and the transmission part may preferably have a connection channel which connects the side facing the drive shaft side and the side facing away from the drive ⁇ shaft side of the bearing together, thus allowing a flow of lubricant supplied on one side.
  • This is particularly useful in a bearing Zvi ⁇ rule of a connecting rod and a crankshaft, within the connecting rod head, is advantageous.
  • an eccentric can be arranged on the crankshaft, which is arranged in the opening in the head of the connecting rod and causes an eccentric movement of the connecting rod.
  • a piston pin in the connecting rod eye can thereby be set in a linear movement.
  • a lubricant main passage in the drive shaft is preferential ⁇ , along the axis of the drive shaft.
  • the lubricant side channels connect the lubricant Hauptka ⁇ nal with the areas in which on the outside of the drive shaft in each case a bearing is arranged.
  • These lubrication ⁇ medium secondary channels can be formed as through holes of the drive shaft or blind holes in the drive shaft.
  • the design of the lubricant channels as a bore in the drive shaft allows easy production.
  • a plurality of lubricant secondary passages can branch off, so that a respective bearing can be supplied more effectively with the lubricant via a plurality of lubricant side passages.
  • a more even distribution of the lubricant and an off ⁇ equal to the lubrication pressure at all operating points is possible.
  • This crank mechanism is intended for use in a fuel pump.
  • a fuel for example, a diesel fuel, used and embedded in the lubricant channels. This use is particularly advantageous because no separate lubricant must be provided is necessary, a separate container is provided for the ge ⁇ optionally, but a portion which is ge ⁇ inflated with the crank drive pump of the fuel is used for lubrication.
  • FIG. 1 shows a transmission part of the crank mechanism in the form of a connecting rod in cross section.
  • FIG. 2 shows the cross section through the connecting rod marked in FIG.
  • FIG. 3 shows an arrangement of a crankshaft and a connecting rod in cross section.
  • FIG. 4 shows a crankshaft with lubricant channels in cross section.
  • FIG. 5 shows the cross section marked in FIG.
  • FIG. 6 shows an alternative embodiment of the crankshaft in a cross section corresponding to FIG.
  • FIG. 7 shows the cross section marked in FIG. 6 for a first further exemplary embodiment.
  • FIG. 8 shows the cross section marked in FIG. 6 for a second further exemplary embodiment.
  • FIG. 9 shows the cross section marked in FIG. 6 for a third further exemplary embodiment.
  • FIG. 10 shows a cross section through a bearing which is provided on the inside with a lubricating groove.
  • FIG. 11 shows a plan view of a bearing provided with a lubricating groove on the outside.
  • FIG. 12 shows a cross section through a bearing according to FIG. 10 for a further exemplary embodiment provided with a connecting channel between the outer and the inner lubricating groove.
  • FIG. 13 shows a plan view of a section of a crankshaft provided with an outer lubrication groove.
  • FIG. 14 is a sectional view showing an arrangement of a crankshaft provided with an external lubrication groove in a housing provided with a lubricant inlet and a crankshaft bearing.
  • 1 shows a cross section of a transmission part, in this example, a connecting rod 1, which is suitable for appli ⁇ dung in the crank mechanism.
  • the connecting rod 1 be ⁇ sits a first opening 8, which is provided for a piston pin and commonly referred to as a connecting rod eye.
  • a piston pin is inserted transversely in this opening 8 and transmits a movement of the connecting rod 1 to a linearly reciprocating piston.
  • Another hole 9 in the so-called small end is for receiving a drive ⁇ wave, for example, a crankshaft, is provided.
  • the on ⁇ drive shaft and the piston pin are guided in a direction perpendicular to the plane of the figure 1 direction through the openings 8 and 9 of the connecting rod 1.
  • the arranged in the opening 9 of the drive shaft is configured be ⁇ sch eccentrically of the axis of the drive shaft so that rotation of the drive shaft causes Rotationsbewe ⁇ supply of the center of the opening. 9
  • This Rotationsbewe ⁇ supply has in the longitudinal direction of the connecting rod, that is, to the connecting rod out a linear component.
  • This BEWE ⁇ supply component can be transferred to a linearly reciprocating piston by means of a angeord ⁇ Neten in the connecting rod gudgeon pin, which in turn drives a pumping mechanism.
  • FIG. 2 shows the marked in the Figure 1 cross-section through the connecting rod, in which again the openings 8, 9 are so ⁇ as the intervening existing lubricant channel 11 visible.
  • FIG. 3 shows a crankshaft 2, which is mounted in a first crankshaft bearing 3 and a second crankshaft bearing 4 and can be rotated about an axis 27 extending horizontally in FIG.
  • the connecting rod 1 is arranged, which is shown in Figure 3 in a cross section corresponding to Figure 2.
  • an associated connecting rod bearing 5 Between the connecting rod 1 and the crankshaft 2 is located in the relevant opening 9 of the connecting rod an associated connecting rod bearing 5.
  • an associated Pleuelaugenlager Between the connecting rod 1 and provided for the further power piston pin 7, which is arranged in the connecting rod, there is an associated Pleuelaugenlager. 6
  • lubricant channels are provided ⁇ seen, which are formed in the embodiment of Figure 3 by ei ⁇ nen arranged in the crankshaft 2 main lubricant channel 12 and a number of lubricant side channels 13, 14, 15 and a lubricant channel 11 in the connecting rod.
  • a lubricant inlet 10 is shown schematically on a En ⁇ de which is also shown only schematically crankshaft. 2
  • the lubricant inlet 10 may also be provided at one or more other locations and be optionally connected via a lubricant channel with the addition Schmiermit ⁇ telmaschinekanal.
  • the lubricants are directed to the bearings via the lubricant channels. It is thus possible direct lubrication of the bearings.
  • a fuel can be In ⁇ play a diesel fuel used for.
  • a prefeed pump 26 is connected to the fuel tank, which generates a Kraftstoffström that can be introduced into the lubricant channels.
  • the Vorför ⁇ derpumpe can be installed separately and driven externally or driven by the same crankshaft 2 as the crank ⁇ drive pump.
  • a pre-feed pump used anyway for filling the crank drive pump is used.
  • the pre-supply pump ges ⁇ tattet it to press the lubricant at a certain vorgese ⁇ Henen pressure in the lubricant feed 10th
  • the main lubricant passage 12 extends along the axis of the crankshaft 2. It is instead possible, the main lubricant passage
  • the main lubricant passage 12 is provided to guide the lubricant to the portions of the crankshaft 2 where each of the various crankshaft bearings are arranged. Arrangements of drainage lines are provided at the points in question, which form the Schmierstoffnebenkanä ⁇ le 13, 14, 15 and their directions also 29ie ⁇ the can be arranged.
  • the lubricant side channels are provided at the points in question, which form the Schmierstoffnebenkanä ⁇ le 13, 14, 15 and their directions also 29ie ⁇ the can be arranged.
  • the connecting rod bearing 5 is lubricated via the lubricant side channel 15. From there, the lubricant can be passed into the lubricant channel 11 of the connecting rod 1. Since ⁇ for there are various ways that are clear from the nachfol ⁇ quietly described examples.
  • a connecting channel 18 in the connecting rod bearing 6 is present in the upper part, passes through the lubricant from the lubricant passage 11 in the region between the Pleuelaugenlager 6 and the piston pin 7.
  • the lubricant side channels 13, 14, 15 are formed in the example of Figure 3 respectively through through holes in the crankshaft 2. But it is also sufficient if a respective lubricant side channel branches off in only one direction from the lubricant central ⁇ main channel 12, so that the arrangement of the lubricant sub-channels not point-symmetrical with respect to Axle of the crankshaft is. Again, further explanations will be given below.
  • Figure 4 shows a cross section corresponding to Figure 3 through the crankshaft 2 alone.
  • the crankshaft 2 is hollow drilled here and thereby the lubricant main channel 12 is formed.
  • it is at the lubricant ⁇ main channel 12 to a blind bore; Instead, however, a through hole is possible.
  • transverse bores are produced as lubricant side passages 13, 14, 15.
  • the cross bores can completely penetrate the bore of the main lubricant channel and the crankshaft; it is sufficient, depending ⁇ but when the transverse bores are formed as blind holes only.
  • FIG. 5 shows the cross section through the crankshaft 2 marked in FIG. 4.
  • the arrangements of the main lubricant channel 12 and of a lubricant secondary channel 14 can be seen, which in this example is designed as a blind hole.
  • FIG. 6 shows an alternative embodiment of the crankshaft 2 in a cross section according to the figure 4, wherein here the lubricant side channels 13, 14, 15 are formed as Naturalgangsbohrun ⁇ conditions.
  • FIG. 7 shows the cross section marked in FIG. In the figure 7, the relative position of the lubricant main ⁇ channel 12 and the lubricant side channel 14 as a passage ⁇ bore in the crankshaft 2 can be seen.
  • FIGS. 8 and 9 show cross sections according to FIG. 7 for embodiments in which the lubricant side channels are of star-shaped design.
  • Such star-shaped Anord ⁇ voltages of the lubricant secondary channels are also possible for exporting ⁇ approximately examples with blind holes.
  • FIG. 10 shows a cross-section by the method described as an example Pleuelkopflager 5.
  • This cross-section is ent ⁇ speaking aligned to the cross section of Figure 3, with the crankshaft 2 and the connecting rod are omitted.
  • the hatched areas of Figure 10 indicate the cut surfaces, while the area shown in between represents the top of the inside of the bearing.
  • an inner lubrication groove 16 of the PleuelkopfIa- gers 5 is provided.
  • This lubrication groove 16 is a groove in the inner surface of the Pleuelkopflagers 5, which is in the cylindrical inner wall of the Pleuelkopflagers 5, for example, half-shaped torpedo.
  • FIG. 11 shows a plan view of a further form of the exporting ⁇ approximately Pleuelkopflagers 5 according to the embodiment shown in Fi gur ⁇ 10 orientation.
  • an outer oil groove 17 is provided, for example, be schtorusförmig ⁇ is fear in the cylindrical outer wall of the Pleuelkopflagers.
  • the bearing can be provided with both an internal lubrication groove and an external lubrication groove. It can also be mounted inside or outside several such lubrication grooves.
  • FIG. 12 shows a further embodiment of the Pleu ⁇ elkopflagers 5, wherein an inner lubrication groove 16 and an outer oil groove 17 are connected to each other and present a Wegska ⁇ nal 18th
  • Such an embodiment is particularly suitable for, for example, in the arrangement shown in Figure 3, the lubricant from the Schmierstoffmaschineka ⁇ nal 12 of the crankshaft 2 in the internal oil groove 16 of the Pleuelkopflagers 5, through the connecting channel 18 in externa ⁇ ßere oil groove 17 of the Pleuelkopflagers 5 and from there into the lubricant channel 11 in the connecting rod 1 to pass.
  • a corresponding connecting channel 28 in the connecting rod bearing 6, as shown in Figure 3, is then suitable to direct the lubricant in the region between the Pleuelaugenlager 6 and the piston pin 7.
  • the contact partners so in this example in the connecting rod 1 and / or the crankshaft 2 and in the connecting rod ⁇ rod 1 and / or the piston pin 7, attached ,
  • the Pleuelaugenla ⁇ ger 6 for example, rigidly connected to the connecting rod 1, so that the compound 28 respectively forms the extension of the lubricant channel 11 to the piston pin 7 out.
  • at least one further oil groove may be in the réelleflä ⁇ surface of the connecting rod eye (opening 8) and / or mounted in the outer surface of Pleuelaugenlagers 6 may be, through which the lubricant is transferred from the lubricant channel 11 in the Verbin ⁇ dung channel 28th
  • the lubrication grooves and connecting channels described with reference to FIGS. 10 to 12 can be provided individually and in different connections with one another also in the other bearings, in particular the first crankshaft bearing 3 or the second crankshaft bearing 4 of FIG.
  • the oil grooves do not need to be arranged in a to the axis of the crankshaft 2 and in a direction perpendicular to the center axis of an opening of the connecting rod 1 level, son ⁇ countries may be oriented obliquely and / or Ver ⁇ two conditions suitable.
  • a lubrication groove may be disposed in the outer surface of the crankshaft 2 or in an inner surface of the connecting rod 1 instead of in the inner surface of a bearing.
  • FIG. 13 shows a lubricating groove 19 in the outer surface of the crankshaft 2, this lubricating groove 19 in this embodiment semi-toroidal and concentric with the axis of the crankshaft 2 is arranged.
  • crankshaft bearing may, for example, be the first crankshaft bearing 3 or the second crankshaft bearing 4 according to FIG.
  • the bearing may, for example, be pressed into the housing 21.
  • the crank ⁇ shaft is provided in this example according to the figure 13 in the outer surface with a lubricating groove 19.
  • the housing 21 is also provided in this example in the region of the bearing 3 with ei ⁇ ner lubricating groove 22.
  • the bearing 3 is in the example shown in Fi ⁇ gur 14 embodiment with a kauska ⁇ nal 23 between the crankshaft 2 and the housing 21 verse ⁇ hen, which in this example in particular, the oil groove 19 of the crankshaft 2 with the oil groove 22 of the housing 21 ver ⁇ binds.
  • a further connecting channel 24 before ⁇ present in this example in the region of the lubricating groove 22.
  • the further connecting channel 24 connects the connecting channel 23 of the bearing and, if present, the lubricating groove 22 of the housing 21 with an externally mounted Lubricant inlet 25. In this way it is possible to attach the lubricant inlet 25 statically on the housing 21 of the crank ⁇ drive.
  • the lubrication grooves 19, 22 may be omitted in principle, but are preferably present in this example.
  • a lubricant inlet is guaranteed to the inside, even if at a relative rotation of the components against each other, in particular the possibly not very rigidly mounted in the housing La ⁇ gers relative to the housing, the connecting channels 23, 24 not in a line stay.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Abstract

L'invention concerne une bielle motrice (1) et un vilebrequin (2), qui sont pourvus de paliers de vilebrequin (3, 4), d'un palier de tête de bielle (5) et/ou d'un palier de pied de bielle (6), et présentent des canaux de lubrifiant (11, 12, 13, 14, 15), avec lesquels un lubrifiant peut être acheminé directement d'une arrivée de lubrifiant (10) jusqu'aux paliers. Avec cet agencement, la lubrification des paliers est essentiellement améliorée et une compensation de la charge des paliers est occasionnée. L'agencement est prévu pour une transmission d'énergie dans des pompes à mécanisme à manivelle, qui sont utilisées en tant que pompes à carburant.
PCT/EP2007/059932 2006-09-28 2007-09-20 Mécanisme à manivelle pour pompe à mécanisme à manivelle et utilisation dans une pompe à carburant WO2008037644A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200610045899 DE102006045899B4 (de) 2006-09-28 2006-09-28 Kurbeltrieb für Kurbeltriebpumpe und Verwendung in einer Kraftstoffpumpe
DE102006045899.0 2006-09-28

Publications (1)

Publication Number Publication Date
WO2008037644A1 true WO2008037644A1 (fr) 2008-04-03

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Application Number Title Priority Date Filing Date
PCT/EP2007/059932 WO2008037644A1 (fr) 2006-09-28 2007-09-20 Mécanisme à manivelle pour pompe à mécanisme à manivelle et utilisation dans une pompe à carburant

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WO (1) WO2008037644A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2113653A1 (fr) * 2008-04-30 2009-11-04 Delphi Technologies, Inc. Pompe à fluides
DE102008046630A1 (de) * 2008-09-10 2010-03-11 Emitec Gesellschaft Für Emissionstechnologie Mbh Modulares Tanksystem für ein flüssiges Reduktionsmittel mit einem Sumpfelement
IT1395606B1 (it) * 2009-09-14 2012-10-16 Bosch Gmbh Robert Pompa ad alta pressione migliorata per alimentare combustibile a un motore a combustione interna e anello di tenuta albero migliorato per la stessa

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB846264A (en) * 1956-01-31 1960-08-31 English Electric Co Ltd Improvements in and relating to electric refrigerator motor-compressor units
DE1227604B (de) * 1956-09-17 1966-10-27 Gen Motors Corp Einrichtung zum Schmieren des Kolbenbolzens eines Schubkolbenverdichters
GB1082686A (en) * 1963-06-27 1967-09-06 J & E Hall Ltd Improvements in and relating to compressors
EP0325693A2 (fr) * 1988-01-25 1989-08-02 Tecumseh Products Company Système de lubrification pour des compresseurs y compris des garnitures d'étanchéité d'arbre
US5038891A (en) * 1990-04-12 1991-08-13 Copeland Corporation Refrigerant compressor
US20020050425A1 (en) * 2000-10-28 2002-05-02 Iversen Frank Holm Piston compressor, particularly hermetically enclosed refrigerant compressor

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB394227A (en) * 1932-11-10 1933-06-22 Neidl Georg Improvements in high speed air and gas compressors
US3160229A (en) * 1962-03-20 1964-12-08 Tokyo Shibaura Electric Co Compresors

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB846264A (en) * 1956-01-31 1960-08-31 English Electric Co Ltd Improvements in and relating to electric refrigerator motor-compressor units
DE1227604B (de) * 1956-09-17 1966-10-27 Gen Motors Corp Einrichtung zum Schmieren des Kolbenbolzens eines Schubkolbenverdichters
GB1082686A (en) * 1963-06-27 1967-09-06 J & E Hall Ltd Improvements in and relating to compressors
EP0325693A2 (fr) * 1988-01-25 1989-08-02 Tecumseh Products Company Système de lubrification pour des compresseurs y compris des garnitures d'étanchéité d'arbre
US5038891A (en) * 1990-04-12 1991-08-13 Copeland Corporation Refrigerant compressor
US20020050425A1 (en) * 2000-10-28 2002-05-02 Iversen Frank Holm Piston compressor, particularly hermetically enclosed refrigerant compressor

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DE102006045899B4 (de) 2009-02-26
DE102006045899A1 (de) 2008-04-03

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